Modular air cooled condenser flow converter apparatus and method

ABSTRACT

The present invention relates to a mechanical draft cooling tower that employs air cooled condenser modules. The aforementioned cooling tower operates by mechanical draft and achieves the exchange of heat between two fluids such as atmospheric air, ordinarily, and another fluid which is usually steam. The aforementioned cooling tower utilizes a modular air cooled condenser concept wherein the air cooled condensers utilize heat exchange deltas and uniquely designed fluid flow dividers.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims priority and is a continuation of U.S. patentapplication entitled Modular Air Cooled Condenser Flow ConverterApparatus and Method, filed Oct. 8, 2014, having a Ser. No. 14/509,687,the disclosure of which is hereby incorporated by reference in itsentirety.

FIELD OF THE INVENTION

The present invention relates to a mechanical draft cooling tower thatutilizes air cooled condenser modules. The aforementioned cooling toweroperates by mechanical draft and achieves the exchange of heat betweentwo fluids such as atmospheric air, ordinarily, and another fluid whichis usually steam or an industrial process fluid or the like. Theaforementioned cooling tower employs flow dividers that allow for theindustrial process fluid to be flowed to multiple tube bundles locatedin the condenser modules efficiently and economically.

BACKGROUND OF THE INVENTION

Cooling towers are heat exchangers of a type widely used to emanate lowgrade heat to the atmosphere and are typically utilized in electricitygeneration, air conditioning installations and the like. In a mechanicaldraft cooling tower for the aforementioned applications, airflow isinduced or forced via an air flow generator such as a driven impeller,driven fan or the like. Cooling towers may be wet or dry. Dry coolingtowers can be either “direct dry,” in which steam is directly condensedby air passing over a heat exchange medium containing the steam or an“indirect dry” type cooling towers, in which the steam first passesthrough a surface condenser cooled by a fluid and this warmed fluid issent to a cooling tower heat exchanger where the fluid remains isolatedfrom the air, similar to an automobile radiator. Dry cooling has theadvantage of no evaporative water losses. Both types of dry coolingtowers dissipate heat by conduction and convection and both types arepresently in use. Wet cooling towers provide direct air contact to afluid being cooled. Wet cooling towers benefit from the latent heat ofvaporization which provides for very efficient heat transfer but at theexpense of evaporating a small percentage of the circulating fluid.

To accomplish the required direct dry cooling the condenser typicallyrequires a large surface area to dissipate the thermal energy in the gasor steam and oftentimes may present several challenges to the designengineer. It sometimes can be difficult to efficiently and effectivelydirect the steam to all the inner surface areas of the condenser becauseof non-uniformity in the delivery of the steam due to system ductingpressure losses and velocity distribution. Therefore, uniform steamdistribution is desirable in air cooled condensers and is critical foroptimum performance. Another challenge or drawback is, while it isdesirable to provide a large surface area, steam side pressure drop maybe generated thus increasing turbine back pressure and consequentlyreducing efficiency of the power plant. Therefore it is desirous to havea condenser with a strategic layout of ducting and condenser surfacesthat allows for an even distribution of steam throughout the condenser,that reduces back pressure, while permitting a maximum of coolingairflow throughout and across the condenser surfaces.

Another drawback to the current air cooled condenser towers is that theyare typically very labor intensive in their assembly at the job site.The assembly of such towers oftentimes requires a dedicated labor force,investing a large amount of hours. Accordingly, such assembly is laborintensive requiring a large amount of time and therefore can be costly.Accordingly, it is desirable and more efficient to assemble as much ofthe tower structure at the manufacturing plant or facility, prior toshipping it to the installation site.

It is well known in the art that improving cooling tower performance(i.e. the ability to extract an increased quantity of waste heat in agiven surface) can lead to improved overall efficiency of a steamplant's conversion of heat to electric power and/or to increases inpower output in particular conditions. Moreover, cost-effective methodsof manufacture and assembly also improve the overall efficiency ofcooling towers in terms of cost-effectiveness of manufacture andoperation. Accordingly, it is desirable for cooling tower that areefficient in both in the heat exchange properties and assembly. Thepresent invention addresses this desire.

Therefore it would desirous to have an economical, mechanical draftcooling tower that is efficient not only in its heat exchange propertiesbut also in its time required for assembly and cost for doing the samewhile minimizing steamside pressure drop relating to the ducting of saidcooling tower.

SUMMARY OF THE INVENTION

Embodiments of the present invention advantageously provides for afluid, usually steam and method for a modular mechanical draft coolingtower for condensing said steam.

In one embodiment of the present invention, a flow divider for thedistribution of a flow of industrial fluid for use in an air cooledcondenser or the like having a vertical axis, the flow dividercomprising: a cylindrical lower base portion that receives the flow ofindustrial fluid; an upper diffusion region that extends from saidcylindrical base portion wherein said upper diffusion region isgenerally non-cylindrical in geometry; a first port disposed on saidupper diffusion region that allows for the flow of industrial fluidthere through; and a first conduit connected to said first port.

In another embodiment of the present invention, an air cooled condenserfor cooling an industrial fluid is provided, comprising: a firstcondenser bundle having a first set of tubes having first and secondends; a steam manifold connected to the third ends of the first settubes; a condensate header connected to said fourth end of the first settubes; a second condenser bundle having a second set of tubes havingthird and fourth ends; a steam manifold connected to the first ends ofthe second set tubes; a condensate header connected to said second endof the second set tubes; a flow divider for the distribution of a flowof industrial comprising: a cylindrical lower base portion that isreceives the flow of industrial fluid; an upper diffusion region thatextends from said cylindrical base portion wherein said upper diffusionregion is generally non-cylindrical in geometry; a first port disposedon said upper diffusion region that allows for the flow of industrialfluid there through; a second port disposed on said upper diffusionregion that allows for the flow of industrial fluid there through and afirst conduit connected to said first port and said first set of tubes;and a second conduit connected to said second port and said first set oftubes.

In yet another embodiment of the present invention, a method fordistributing a fluid to be cooled using a flow divider is provided,comprising: receiving the fluid to be cooled through a cylindrical lowerbase portion that; flowing the fluid to be cooled through an upperdiffusion region that extends from said cylindrical base portion whereinsaid upper diffusion region is generally non-cylindrical in geometry;flowing the fluid to be cooled through a first port disposed on saidupper diffusion region; and flowing the fluid to be cooled through afirst conduit connected to said first port.

In still another embodiment of the present invention, a flow divider foruse with an air cooled condenser or the like is provided, comprising:means for receiving the fluid to be cooled through a cylindrical lowerbase portion; means for flowing the fluid to be cooled through an upperdiffusion region that extends from said cylindrical base portion whereinsaid upper diffusion region is generally non-cylindrical in geometry;means for flowing the fluid to be cooled through a first port disposedon said upper diffusion region; and means for flowing the fluid to becooled through a first conduit connected to said first port.

In another embodiment of the present invention, a multi-delta air cooledcondenser for cooling an industrial fluid or the like is provided,comprising: a first street that comprises a first air cooled condensermodule; a second street comprising a second air cooled condenser module;a first central duct that is in fluid communication with said first aircooled condenser module and said second air cooled condenser module; athird street comprising a third air cooled condenser module; a secondcentral duct that is in fluid communication with said third air cooledcondenser module; a first flow divider connected to said first centralduct, comprising: a cylindrical lower base portion that receives theflow of industrial fluid; an upper diffusion region that extends fromsaid cylindrical base portion wherein said upper diffusion region isgenerally non-cylindrical in geometry; a first port disposed on saidupper diffusion region that allows for the flow of industrial fluidthere through; and a first conduit connected to said first port, whereinsaid first conduit is in fluid communication with said first air cooledcondenser module; a second port disposed on said upper diffusion regionthat allows for the flow of industrial fluid there through; and a secondconduit connected to said first port, wherein said first conduit is influid communication with said second air cooled condenser module; asecond flow divider connected to said second central duct, comprising: acylindrical lower base portion that is receives the flow of industrialfluid; an upper diffusion region that extends from said cylindrical baseportion wherein said upper diffusion region is generally non-cylindricalin geometry; a third port disposed on said upper diffusion region thatallows for the flow of industrial fluid there through; and a thirdconduit connected to said third port, wherein said third conduit is influid communication with said third air cooled condenser module.

In still another embodiment of the present invention, a quick connectioncoupling for use with an air cooled condenser is provided, comprising: acollar having a first half and; a second half hingedly connected to saidfirst half an internal sealing piece having a circumference that isdisposed within said first half and said second half a sealing memberthat encircles the circumference; and a releasable attachment memberthat releasably attaches said first half to said second half.

In an embodiment of the present invention, a method of retaining a firstconduit and a second conduit wherein each conduit has a flange isprovided, comprising: inserting the first and second conduit into aconnection coupling, comprising: a collar having a first half; a secondhalf hingedly connected to said first half; an internal sealing piecehaving a circumference that is disposed within said first half and saidsecond half; a sealing member that encircles the circumference; and areleasable attachment member that releasably attaches said first have tosaid second half; encircling each conduit with the internal sealingpiece; engaging each flange with the first half and the second half suchthat the conduits are retained; and tightening the attachment membersuch that the collar sealingly retains the conduits.

In still another embodiment of the present invention, a flow divider forthe distribution of a flow of industrial fluid for use in an air cooledcondenser or the like having a vertical axis is provided, the flowdivider comprising: a cylindrical lower base portion that provides aninlet that receives the flow of industrial fluid, wherein saidcylindrical base portion has a first diameter; a first truncated coneextending from said lower base portion wherein said first truncated conehas a first end and a second end and wherein said first truncated conetransitions from one diameter to another as said cone extends from saidfirst end to said second end; a second truncated cone extending fromsaid lower base portion wherein said second truncated cone has a thirdend and a fourth end and wherein said second truncated cone transitionsfrom one diameter to another as said cone extends from said third end tosaid fourth end; a first conduit connected to said first truncated cone,wherein said first conduit has a second diameter; and a second conduitconnected to said second truncated cone, wherein said second conduit hasa third diameter.

In another embodiment of the present invention, an air cooled condenserfor cooling an industrial fluid is provided, comprising: a firstcondenser bundle having a first set of tubes having first and secondends; a steam manifold connected to the first ends of the first settubes; a condensate header connected to said second end of the first settubes; a second condenser bundle having a second set of tubes havingfirst and second ends; a steam manifold connected to the first ends ofthe second set tubes; a condensate header connected to said second endof the second set tubes; a flow divider, comprising: a cylindrical lowerbase portion that provides an inlet that receives the flow of industrialfluid, wherein said cylindrical base portion has a first diameter; afirst truncated cone extending from said lower base portion wherein saidfirst truncated cone has a first end and a second end and wherein saidfirst truncated cone transitions from one diameter to another as saidcone extends from said first end to said second end; a second truncatedcone extending from said lower base portion wherein said secondtruncated cone has a third end and a fourth end and wherein said secondtruncated cone transitions from one diameter to another as said coneextends from said third end to said fourth end; a first conduitconnected to said first truncated cone, wherein said first conduit has asecond diameter and is in fluid communication with said first tubebundle; and a second conduit connected to said second truncated cone,wherein said second conduit has a third diameter and is in fluidcommunication with said second tube bundle.

In yet another embodiment of the present invention, a method ofretaining a first conduit and a second conduit wherein each conduit hasa flange is provided, comprising: inserting the first and second conduitinto a connection coupling, comprising: a collar having a first half; asecond half hingedly connected to said first half; an internal sealingpiece having a circumference that is disposed within said first half andsaid second half; a sealing member that encircles the circumference; anda releasable attachment member that releasably attaches said first haveto said second half; encircling each conduit with the internal sealingpiece; engaging each flange with the first half and the second half suchthat the conduits are retained; and tightening the attachment membersuch that the collar sealingly retains the conduits.

There has thus been outlined, rather broadly, certain embodiments of theinvention in order that the detailed description thereof herein may bebetter understood, and in order that the present contribution to the artmay be better appreciated. There are, of course, additional embodimentsof the invention that will be described below and which will form thesubject matter of the claims appended hereto.

In this respect, before explaining at least one embodiment of theinvention in detail, it is to be understood that the invention is notlimited in its application to the details of construction and to thearrangements of the components set forth in the following description orillustrated in the drawings. The invention is capable of embodiments inaddition to those described and of being practiced and carried out invarious ways. Also, it is to be understood that the phraseology andterminology employed herein, as well as the abstract, are for thepurpose of description and should not be regarded as limiting.

As such, those skilled in the art will appreciate that the conceptionupon which this disclosure is based may readily be utilized as a basisfor the designing of other structures, methods and systems for carryingout the several purposes of the present invention. It is important,therefore, that the claims be regarded as including such equivalentconstructions insofar as they do not depart from the spirit and scope ofthe present invention.

BRIEF DESCRIPTION OF THE DRAWINGS

The above-mentioned and other features and advantages of thisdisclosure, and the manner of attaining them, will become more apparentand the disclosure itself will be better understood by reference to thefollowing description of various embodiments of the disclosure taken inconjunction with the accompanying figures.

FIG. 1 is a perspective view of an air cooled condenser modules inaccordance with an embodiment of the present invention.

FIG. 2 is a perspective, plan view of the air cooled condenser modulesdepicted in FIG. 1 in accordance with an embodiment of the presentinvention.

FIG. 3 is a perspective view of a fluid flow divider in accordance withan embodiment of the present invention.

FIG. 4 is a perspective view of an alternative embodiment of a fluidflow divider in accordance with an embodiment of the present invention.

FIG. 5 is a schematic view of a flow divider geometry in accordance withan embodiment of the present invention.

FIG. 6 is a schematic view of a flow divider geometry in accordance withanother embodiment of the present invention.

FIG. 7 is a schematic view of a flow divider geometry in accordance withyet another embodiment of the present invention.

FIG. 8 is a schematic depiction of a street configuration for an aircooled condenser in accordance with an embodiment of the presentinvention.

FIG. 9 is a schematic depiction of a street configuration for an aircooled condenser in accordance with another embodiment of the presentinvention.

FIG. 10 is a perspective view of a quick connection for an air cooledcondenser in accordance with an embodiment of the present invention.

FIG. 11 is a perspective view of a clamp of the quick connectiondepicted in FIG. 10.

FIG. 12 is a perspective view of a flow divider in accordance with analternative embodiment of the present invention.

FIG. 13 is another perspective view of the flow divider depicted in FIG.12.

DETAILED DESCRIPTION OF THE INVENTION

In the following detailed description, reference is made to theaccompanying drawings, which form a part hereof and show by way ofillustration specific embodiments in which the invention may bepracticed. These embodiments are described in sufficient detail toenable those skilled in the art to practice them, and it is to beunderstood that other embodiments may be utilized, and that structural,logical, processing, and electrical changes may be made. It should beappreciated that any list of materials or arrangements of elements isfor example purposes only and is by no means intended to be exhaustive.The progression of processing steps described is an example; however,the sequence of steps is not limited to that set forth herein and may bechanged as is known in the art, with the exception of steps necessarilyoccurring in a certain order.

Turning now to FIG. 1, a sectional view of a series of air cooledcondenser modules of an air cooled condenser, generally designated 10,is illustrated. The air cooled condenser modules 10 include multipleA-type geometry deltas, each designated 12 and 14 respectively. Twodeltas are identified for ease of description and explanation howeverthe condenser modules employ numerous deltas depending upon the size ofthe air cooled condenser tower and/or the application of the air cooledcondenser tower. Each delta 12, 14 comprises two tube bundle assemblies15 having a series of finned tubes to conduct heat transfer. The deltas12, 14 will be discussed in further detail below.

Referring now to FIGS. 1-3, the flow divider, generally designated 32,is depicted. Whereas the flow divider 32 is illustrated in combinationwith the A-type deltas in FIGS. 1 and 2, the flow divider 32 isillustrated in isolation in FIG. 3 so as all the components and geometrycan be easily viewed and described. In the embodiment depicted FIGS.1-3, the flow divider 32 functions to feed four finned tube bundles 15(two bundles per delta 12, 14). As illustrated, the flow divider 32comprises a base portion, generally designated 35, from which a seriesof conduits 24, 26, 28, 30 extend. Each conduit 24, 26, 28, 30 has acurved “elbow” shape design and connects to a respective feed conduit16, 18, 20, 22. Each of the feed conduits 16, 18, 20, 22 is connectedto, and in fluid communication with, the A-type deltas 12, 14, and morespecifically, the finned tube bundles 15.

The flow divider 32 is comprised two portions or regions havinggeometries or designs distinct from one another. The flow divider 32 hasa lower cylindrical base portion or region 34 wherein the main flow ofthe industrial fluid enters said fluid divider 32. The lower baseportion or region 34 transitions to a diffusion region 36 which has agenerally square geometry. As depicted in FIGS. 1-3, and morespecifically in FIG. 3, the diffusion section 36 includes several holesor ports that coincide with the elbow conduits 24, 26, 28, 30 whereineach allows for the flow of industrial fluid there through. A typicalair cooled condenser employs risers to which each flow divider 32 isconnected and accordingly allows flow of industrial fluid, such assteam, there through. The risers are connected to a main steam duct ofthe air cooled condenser.

The flow divider 32 functions to divide and/or merge the flows of theindustrial fluid by switching inlet and outlet conduits extending fromsaid divider 32. The divider 32 may have any number of dividing ormerging flows depending upon the size and application of the divider 32.Moreover, the flow divider 32 may employ guiding vanes within the baseportion 34 and/or the diffusion region 36 which assist the reduction ofhead loss. Also, the elbow conduits may vary in design and geometry. Forexample, some embodiments may employ standard elbow conduits, or shortelbow conduits or mitered elbow conduits. Alternatively, “T” piece or“Y” fork designs may be utilized.

Turning back to FIG. 1, a delta 12, 14 will be described in furtherdetail. As depicted, each delta 12, 14 is comprised of two individualheat exchange bundle assemblies 28, each having a series of finnedtubes. The individual tubes are approximately two (2) meters in lengthwhereas the bundle length is approximately twelve (12) meters. Asillustrated, each bundle assembly 15 is positioned at an angle to oneanother to form the A-type configuration of the delta 12, 14. While thebundle assemblies 15 may be positioned at any desired angle, theypreferably are positioned at an angle approximately twenty degrees (20°)to approximately thirty degrees (30°) from vertical and approximatelysixty degrees (60°) to approximately seventy degrees (70°) fromhorizontal. More specifically, the bundle assemblies 15 are positionedat twenty-six degrees (26°) from vertical and sixty-four degrees (64°)from horizontal.

Each of the bundle assemblies 15 may be assembled prior to shippingwherein each typically comprises a riser to header transition piece,steam manifold, finned tubes, and steam condensate headers. Theembodiments of the current invention can utilize five (5) times thetubes, and also employ condenser tubes that are much shorter in length.As result of the aforementioned design and orientation, the steamvelocity traveling through the tube bundles 15 is reduced as result ofthe increased number of tubes in combination with the reduced tubelength, and therefore steam pressure drop within the deltas 12, 14 isreduced, making the air cool condenser 10 more efficient.

Turning now to FIG. 4, an alternative embodiment of the flow divider isdepicted, generally designated 40. Whereas the flow divider designdepicted in FIGS. 1-3 employs four elbow conduits 24, 26, 28, 30, theflow divider 40 depicted in FIG. 4 employs two elbow conduits 46, 48.Like the embodiment illustrated in FIGS. 1-3, the flow divider has alower cylindrical base portion or region 42 wherein the main flow of theindustrial fluid enters said fluid divider 40. The lower base portion orregion 42 transitions to a diffusion region 44, similar to thatdescribed in connection with FIGS. 1-3, having a geometry that isgenerally rectangular in design. As illustrated in FIG. 4, the diffusionsection 44 includes two holes or ports that coincide with elbow conduits46, 48 and allow for flow of industrial fluid there through.

Referring now to FIGS. 5-7 plan views of alternative geometricconfigurations of flow dividers 50 are depicted. As illustrated, theelbow flow conduits, generally 52, may be oriented in multipleconfigurations as desired or needed per the air cooled condenserapplication. FIG. 5 illustrates the flow conduits 52 in a symmetricalorientation, parallel to one another whereas FIG. 6 illustrates the flowconduits 52 positioned equidistant from one another about the flowdivider 54. Finally, FIG. 7 depicts a non-symmetrical orientation.Moreover, the flow conduits may be non-symmetrical in diameter whereinin one embodiment of the present invention, the size of the conduits maybe smaller in diameter whereas other conduits may be larger in diameter.

Turning now to FIG. 8, a schematic view of street arrangements,generally designated 60, for an air cooled condenser is illustrated inaccordance with an embodiment of the present invention. FIG. 8 depicts atop view for an even number of streets, 62 64, 66, 68 whereas FIG. 9illustrates an air cooled condenser set up having an odd number whichwill be discussed in more detail below. Referring back to FIG. 8, thestreets 62, 64, 66, 68 are comprised of a series of cooling modules orcells 70. The cooling modules 70 are connected to, and in fluidcommunication with, the central duct 72 and 73 which flows industrialprocess fluid to the modules 70 to be cooled. The modules 70 comprise ofmultiple A-type geometry deltas similar to those discussed in connectionwith FIG. 1. Each delta 12, 14 comprises two tube bundle assemblies 15(See FIG. 1) with a series of finned tubes to conduct heat transfer. Notshown is the process feeding the process fluid to the central duct 72,73 such as exhaust steam from steam turbines.

As illustrated in FIG. 8, the fluid to be cooled flows to each cell 70via the central duct 72, 73 as previously described. The industrialfluid, such as turbine exhaust, is distributed to the central duct 72,73 which is typically suspended under the air cooled condenser fan decklevel. The central duct 72, 73 feeds the two streets 62, 64 and 66, 68as indicated by the arrows through a series of risers and flow dividers,similar to those described in connection with FIG. 2. The flow dividers,which are designated schematically by reference numeral 74, function tofeed four (4) finned tube bundles 15 (two bundles per delta 12, 14) asdiscussed in connect with FIGS. 1-3. As previously described, each flowdivider 74 comprises a base portion, from which a series of fourconduits extend where two conduits feed one module 70, one conduit foreach side of the A-type geometry delta, and the two other conduits feedthe opposing cell, again, one conduit for each side of the A-typegeometry delta. As previously described, each conduit has a curved“elbow” shape design and connects to a respective feed conduit. Each ofthe feed conduits is connected to, and in fluid communication with theA-type deltas, and more specifically, the finned tube bundles.

Each of the flow dividers 74 is composed to two portions or regionshaving geometries or designs distinct from one another as previouslydiscussed and described. The fluid flow divider 74 has a lowercylindrical base portion or region 34 wherein the main flow of theindustrial fluid enters said fluid divider 74. The lower base portion orregion 34 transitions to a diffusion region which has a generally squaregeometry. This diffusion section includes several holes or ports thatcoincide with the elbow conduits and allow for flow of industrial fluidthere through.

Turning now to FIG. 9, whereas FIG. 8 depicted an air cooled condenser60 with an even number of streets 62, 64, 66, 68, FIG. 9 depicts aschematic plan view of an air cooled condenser 80 having an odd ornon-even number of streets 82, 84, 86. The streets 82, 84, 86 arecomprised of a series of cooling modules or cells 70 similar to thosediscussed in connection with FIG. 8. The cooling modules 70 areconnected to, and in fluid communication with, the central duct 88 and90 which flows industrial process fluid to the modules 70 to be cooled.The modules comprise of multiple A-type geometry deltas as discussed inconnection with FIG. 1. Each delta 12, 14 comprises two tube bundleassemblies 15 with a series of finned tubes to conduct heat transfer.The cooling modules 70 are connected to, and in fluid communicationwith, the central duct 88, 90 that flows industrial process fluid to themodules 70 to be cooled (See FIG. 1). The modules include multipleA-type geometry deltas as discussed in connection with FIG. 1. Eachdelta 12, 14 comprises two tube bundle assemblies 15 with a series offinned tubes to conduct heat transfer. Not shown is the process feedingthe process fluid to the central duct 88, 90 such as exhaust steam fromsteam turbines.

Similar to the embodiment discussed in connection with FIG. 8, the fluidto be cooled flows to each module 70 via the central duct 88, 90 aspreviously described. The industrial fluid, such as turbine exhaust, isdistributed to the central duct 88, 90 which is typically suspendedunder the air cooled condenser fan deck level. As illustrated in FIG. 9the central duct 88 feeds streets 84 and 86, while the central duct 90feeds streets 82 and 84 as indicated by the arrows. The aforementionedflow is achieved through a series of risers and flow dividers, similarto those described in connection with FIGS. 3 and 4. The flow dividers,which are designated schematically at the intersection of the centralducts and the arrows, reference numerals 92 and 94. Each functions tofeed finned tube bundles 15 as discussed in connect with FIGS. 1-3. Ascan be seen in FIG. 9, the flow dividers designated with referencenumeral 92 feed two streets, streets 84 and 86 or streets 82 and 84whereas the flow dividers 94 feed a single street.

The flow dividers 92 will be described in connection with the embodimentdepicted in FIGS. 1-3, wherein each comprises a base portion, generallydesignated 35, from which a series of conduits 24, 26, 28, 30 extend.Each conduit 24, 26, 28, 30 has a curved “elbow” shape design andconnects to a respective feed conduit 16, 18, 20, 22. Each of the feedconduits 16, 18, 20, 22 is connected to, and in fluid communication withthe A-type deltas 12, 14, and more specifically, the finned tube bundles15.

The flow divider 92 is composed to two portions or regions havinggeometries or designs distinct from one another. The flow divider 92 hasa lower cylindrical base portion or region 34 wherein the main flow ofthe industrial fluid enters said flow divider 92. The lower base portionor region 34 transitions to a diffusion region 36 which has a generallysquare geometry. As depicted in FIG. 3, the diffusion section 36includes several holes or ports that coincide with the elbow conduits24, 26, 28, 30 and allow for flow of industrial fluid there through. Atypical air cooled condenser employs risers to which the flow divider 32is connected and accordingly allows flow of industrial fluid, such assteam, there through. The risers are connected to a main steam duct.

The flow divider 92 functions to divide and/or merge the flows byswitching inlet and outlet conduits extending from said divider 92. Thedivider 92 may have any number of dividing or merging flows dependingupon the size and application. Moreover, the flow divider 92 may employguiding vanes within the base portion 34 and/or diffusion region 36which assist the reduction of head loss. Also, the elbow conduits mayvary in design and geometry. For example, some embodiments may employstandard elbow conduits, or short elbow conduits or mitered elbowconduits.

Turning now to the flow dividers designated by the reference numeral 94,said flow dividers are similar to the embodiment illustrated in FIG. 4and will be described in connection with FIG. 4. Whereas the flowdivider design depicted in FIGS. 1-3 employs four elbow conduits 24, 26,28, 30, the flow divider 40 depicted in FIG. 4 employs two elbowconduits 42, 44. The flow divider 92 has a lower cylindrical baseportion 42 or region wherein the main flow of the industrial fluidenters said flow divider 92. The lower base portion or region 42transitions to a diffusion region 44, having a geometry that isgenerally rectangluar in design. As illustrated in FIG. 4, the diffusionsection 44 includes two holes or ports that coincide with elbow conduits46, 48 and allow for flow of industrial fluid there through.

In the orientation described in FIGS. 8 and 9, the steam distributionhas been adapted such the central ducts 88, 90 have the same diameter.In the depicted orientation, the central ducts operate to feed steam toone street of one side of the central duct and half of the street on theon the other side of the central duct. Therefore, one central duct isfeeding two modules each of the central duct and then alternating to onemodule each of side and so on and so forth.

Turning now to FIGS. 10 and 11, a quick connection design, generallydesignated 200, is illustrated. The quick connection includes a collar210 and an internal sealing piece 212 that rests in, and is secured bythe collar 210. The internal sealing piece 212 is generally circular indiameter and has a sealing component 214 such as an O-ring or the like,which provides sealing engagement between two conduits which will bediscussed in further detail below. As illustrated in FIGS. 10 and 11,the collar 210 includes two halves or pieces 216, 218 connected via aswivel or hinge 220 at one end of the collar. The collar 210 alsoincludes a sealing attachment of each side at the other end via anattachment mechanism 222. This attachment 222 is adjustable and in oneembodiment, a nut and bolt combination is preferred.

Due to the fact that air cooled condenser typically operate under vacuumconditions, all connections obviously must be tight and secure. The mostcommon way to provide a tight connection is welding the tubes orconduits together. The quick connection design is an alternative towelding. Accordingly, during operation, the collar 210 captures theflanges of two conduits 224, 226 wherein the sealing component functionsto encircle the ends of each respective conduit. The collar 210 is thentightened around said sealing component via the adjustable attachment222, sealing the conduits together. Quick connection can be employed onair cooled condensers in several connection applications for examplecondensate lines, air take off lines, and steam lines. Quick connectionscan be installed by less skilled personnel than required for weldingwhich is very important especially when skilled personnel is in shortsupply.

During operation, typically, turbine back pressure of the air cooledcondenser or the like is limited by the maximum steam velocity in thetubes (to limit erosion) wherein the steam velocity is increasing with adecrease of back pressure (due to density of steam). Thus, due to theaddition of tubes as described in the present invention in combinationwith the flow divider design, the steam is still maintained at themaximum allowable steam velocity but at a lower back pressure. Anotherlimitation the current delta design addresses is that the pressure atthe exit of the secondary bundles cannot be less than the vacuum pumpcapability. This pressure typically results from turbine back pressureminus the pressure drop in ducting minus the pressure drop in the tubes.Accordingly, due to the reduced pressure drop in the tubes, theallowable turbine back pressure is lower with the propose air cooledcondenser design.

Furthermore, the above-described bundle design also reduces the pressuredrop within the individual delta 12, 14. For example, the heat exchangethat takes place via the deltas 12, 14, is dependent upon the heatexchange coefficient, i.e., the mean temperature difference between airand steam and the exchange surface. Due to the reduced pressure drop aspreviously described, the mean pressure (average between inlet pressureand exit pressure) in the exchanger is higher with the design of theproposed air cooled condenser. In other words, because steam issaturated, the mean steam temperature is also higher for the same heatexchange surface resulting in increased heat exchange.

Alternatively, the above described embodiments of the present employtube bundles manufactured and assembled, prior to shipping, having steammanifold and steam condensate headers, alternative embodiment bundlesmay not include a manifold prior to shipping. More specifically, in suchembodiments, the tube bundles may be ship without steam manifoldsattached thereto. In said embodiments, the tube bundles may be assembledin field to form the A-type configuration, as discussed above. However,instead of employing two steam manifolds, this alternative embodimentmay employ a single steam manifold wherein the single steam manifoldextends along the “apex” of the A configuration.

Turning now to FIGS. 12 and 13, a tee piece or flow divider 300 isillustrated in accordance with an alternative embodiment of the presentinvention. As illustrated in FIGS. 10 and 11, the flow divider 300 has amain cylindrical portion or base 302 that provides a flow inlet. Theflow divider 300 also comprises first and second flow branches eachconnected to, and extending from, the main cylindrical portion 302. Theflow branches 304, 306 as illustrated have a geometry similar totruncated cone regions, 304 and 306 respectively, having a first regionhaving a first diameter that transitions to a second region having asmaller diameter. As can be seen in FIGS. 10 and 11, the flow branchportions 304, 306 may alternatively be described as a melding orcombination or merger of flow regions having a “T” geometry and a “Y”geometry. Also as illustrated in FIGS. 10 and 11, the flow divider 300includes cylindrical portions, 308 and 310, attached to a respectivebranch 304, 306. Said cylindrical portions 308, 310 have a diameter thatis less than the diameter of the inlet portion 302.

The above-described design requires less manufacture time, while alsoproviding a lighter design allowing for less fluid side pressure drop.This present solution should also be more easily cut in piece andre-welded on site. Therefore, the current piece should be easilymanufactured as it is constructed from simple pieces. Moreover, theabove-described divider 200 design minimizes steam side pressure dropsduring operation of an air cooled condenser or the like.

As clearly illustrated in Table 1 below, three flow divider or ductriser connections: Design A, Design B and Design C. Design A is astandard “T” shape design currently used in the art whereas Design B isanother “T” shaped design that utilizes flow vanes whereas Design C isthe flow divider 300 of the present invention. As illustrated in theTable 1, Design C, or the flow divider 300 providing significantimprovement steam side pressure drop wherein it demonstrated 33 percentrelative to the pressure loss coefficient, K for Design A. For Design B,demonstrated 90 percent relative to the pressure loss coefficient, K forDesign A.

TABLE 1 Flow Divider Connection References Design A Design B Design CConditions CFD - RESULTS K — 0.730 0.654 0.239 Relative % 100% 90% 33%

The many features and advantages of the invention are apparent from thedetailed specification, and, thus, it is intended by the appended claimsto cover all such features and advantages of the invention which fallwithin the true spirit and scope of the invention. Further, sincenumerous modifications and variations will readily occur to thoseskilled in the art, it is not desired to limit the invention to theexact construction and operation illustrated and described, for examplea forced draft air cooled condenser has been illustrated but an induceddraft design can be adapted to gain the same benefits and, accordingly,all suitable modifications and equivalents may be resorted to that fallwithin the scope of the invention.

What is claimed is:
 1. A flow divider for the distribution of a flow ofindustrial fluid for use in an air cooled condenser or the like having avertical axis, the flow divider comprising: a cylindrical lower baseportion that provides an inlet that receives the flow of industrialfluid, wherein said cylindrical base portion has a first diameter; afirst truncated cone extending from said lower base portion wherein saidfirst truncated cone has a first end and a second end and wherein saidfirst truncated cone transitions from one diameter to another as saidcone extends from said first end to said second end; a second truncatedcone extending from said lower base portion wherein said secondtruncated cone has a third end and a fourth end and wherein said secondtruncated cone transitions from one diameter to another as said coneextends from said third end to said fourth end; a first conduitconnected to said first truncated cone, wherein said first conduit has asecond diameter; and a second conduit connected to said second truncatedcone, wherein said second conduit has a third diameter.
 2. The flowdivider according to claim 1, wherein said first end of said truncatecone is connected to said lower base portion and said third end of saidsecond truncated cone is connected to said lower base portion.
 3. Theflow divider according to claim 1, wherein said second diameter is lessthan said first diameter.
 4. The flow divider according to claim 3,wherein said third diameter is less than said first diameter.
 5. Theflow divider according to claim 4, wherein said second and said thirddiameters are equal.
 6. The flow divider according to claim 1, whereinsaid first end of said first truncated cone has a diameter and saidsecond end has a diameter that is less than said first end diameter. 7.The flow divider according to claim 6, wherein said third end of saidsecond truncated cone has a diameter and said fourth end has a diameterthat is less than said third end diameter.
 8. The flow divider accordingto claim 1, wherein said flow divider has a “Y” shaped geometry.
 9. Anair cooled condenser for cooling an industrial fluid, comprising: afirst condenser bundle having a first set of tubes having first andsecond ends; a steam manifold connected to the first ends of the firstset tubes; a condensate header connected to said second end of the firstset tubes; a second condenser bundle having a second set of tubes havingfirst and second ends; a steam manifold connected to the first ends ofthe second set tubes; a condensate header connected to said second endof the second set tubes; a flow divider, comprising: a cylindrical lowerbase portion that provides an inlet that receives the flow of industrialfluid, wherein said cylindrical base portion has a first diameter; afirst truncated cone extending from said lower base portion wherein saidfirst truncated cone has a first end and a second end and wherein saidfirst truncated cone transitions from one diameter to another as saidcone extends from said first end to said second end; a second truncatedcone extending from said lower base portion wherein said secondtruncated cone has a third end and a fourth end and wherein said secondtruncated cone transitions from one diameter to another as said coneextends from said third end to said fourth end; a first conduitconnected to said first truncated cone, wherein said first conduit has asecond diameter and is in fluid communication with said first tubebundle; and a second conduit connected to said second truncated cone,wherein said second conduit has a third diameter and is in fluidcommunication with said second tube bundle.
 10. The flow divideraccording to claim 9, wherein said first end of said truncate cone isconnected to said lower base portion and said third end of said secondtruncated cone is connected to said lower base portion.
 11. The flowdivider according to claim 9, wherein said second diameter is less thansaid first diameter.
 12. The flow divider according to claim 11, whereinsaid third diameter is less than said first diameter.
 13. The flowdivider according to claim 12, wherein said second and said thirddiameters are equal.
 14. The flow divider according to claim 1, whereinsaid first end of said first truncated cone has a diameter and saidsecond end has a diameter that is less than said first end diameter. 15.The flow divider according to claim 14, wherein said third end of saidsecond truncated cone has a diameter and said fourth end has a diameterthat is less than said third end diameter.
 16. The flow divideraccording to claim 9, wherein said flow divider has a “Y” shapedgeometry.
 17. The flow divider according to claim 9, further comprisinga flow vane disposed within said cylindrical lower base portion.
 18. Theflow divider according to claim 17, said flow vane is a plurality offlow vanes.
 19. A method for distributing a fluid to be cooled using aflow divider, comprising: receiving the fluid to be cooled through a acylindrical lower base portion that provides an inlet that receives theflow of industrial fluid, wherein said cylindrical base portion has afirst diameter; flowing the fluid to be cooled through an upperdiffusion region that extends from said cylindrical base portion whereinsaid upper diffusion region is generally non-cylindrical in geometry;flowing the fluid to be cooled through a first truncated cone extendingfrom said lower base portion wherein said first truncated cone has afirst end and a second end and wherein said first truncated conetransitions from one diameter to another as said cone extends from saidfirst end to said second end; flowing the fluid to be cooled through asecond truncated cone extending from said lower base portion whereinsaid second truncated cone has a third end and a fourth end and whereinsaid second truncated cone transitions from one diameter to another assaid cone extends from said third end to said fourth end a cylindricallower base portion that provides an inlet that receives the flow ofindustrial fluid, wherein said cylindrical base portion has a firstdiameter; flowing the fluid through a first conduit connected to saidfirst truncated cone, wherein said first conduit has a second diameter;and flowing the fluid a second conduit connected to said secondtruncated cone, wherein said second conduit has a third diameter. 20.The method according to claim 19, wherein said first end of saidtruncate cone is connected to said lower base portion and said third endof said second truncated cone is connected to said lower base portion.